Continuous gear grinding machine



July 12, 1949.- P. KLAMP CONTINUOUS GEAR GRINDING MACHINE 5 Sheets-Sheet 1 Filed Sept. 5, 1946 INVENTOR.

WANv

Juiy 12, 1949.

Filed sept.' 5, 194e P. KLAMP CONTINUOUS GEAR GRINDING MACHINE 5 Sheets-Sheet 2 INVENTOR. 72m; /fZW/.

July 12, 1949. P, KLAMP CONTINUOUS GEAR GRINDING MACHINE 5 Sheets-Sheet 3 Filed Sept. 5, 1946 INVENTOR. Jz/Z- fla/rrp.

' July l2, 1949.

P.\ KLAMP CONTINUOUS GEAR GRINDING MACHINE 5 sheets-sneek; 4

Filed sept. 5, 194e I INV'ENTOR. )VazzZ /fZW/v' Qhu.

, i Trax/515145.

July l2, P .KLAMP v CONTINUOUS GEAR GRINDING MACHINE Filed Sept. 5, 1946 5 Sheets-Sheet 5 Patented .uly 12, 1949 PATENT OFFICE CNTINUOUS GEAR GRINDING MACHINE.

Paul Klamp, Detroit, Mich., assigner to The Cross Company, Detroit, Mich., a corporation of Michigan application september 5, 1946, sferia1No.694,942

19 Claims.

This invention relates broadly to continuous gear-grinding machines.

Gears of hardened metal are more durable than gears that have not been hardened. However, the hardening of gears ytends to distort the accurate form of the teeth. Therefore, it is desirable to leave grinding stock when cutting the teeth, then harden the gears and finish the teeth by a grindlng operation.

An important object of the present invention is to provide a gear-grinding machine that is faster and more efficient than conventional equipment.

Another object of the invention is to provide a gear-grinding machine that operates continuously and eliminates idle periods required for the return stroke `of the grinding wheel and for operation of gear indexing mechanism in conventional reciprocating type gear grinders.

Still another object of the invention is to provide a machine of the above-mentioned character that acts .upon the gear form in suchmanner that both sides of the teeth are ground simultaneously and symmetrically.

Yet another object of the invention is to provide a machine of the above-mentioned character that divides the removal of stock and distributes wear on the grinding wheel by uniquely iorining the latter and associa-ting it with the work in such man-ner that multiple contact points are established therebetween.

A further object of the invention is to provide a machine of the above-mentioned character that includes lmechanism for quickly and eiiciently dressing the grinding wheel.

A still further object of the invention is to pro vide a grinding machine of the above-mentioned character that is capable of handling spur or helical gears, ratchet wheels, saw teeth', slotting cutters, external, involute, blind-end teeth on pinions or spline shafts and the like.

A yet further object of the invention is to pron vide a machine of the above-mentioned character that can be readily adapted for grinding teeth in a solid gear blank.

Other objects and advantages ci the invention will be apparent during the course of the followu ing description.

In the drawings forming a part of this specication and wherein like numerals are employed to designate like parts throughout the same,

Fig. 1 is a -front elevational View of a continuous gear-grinding machine embodying the invention;

Fig. 2 is an enlarged top plan view thereof, parts being broken away and shown insection for lclearness of illustration;

Figs. 3 and. 4 'are` enlarged, iront elevational views showing adiacent 4halves of the machine,

2 parts thereof being broken 'away and shown in section;

Fig. 5 is an enlarged, vertical sectional View taken on the line 5`'5 of Fig. 1;

Fig. 6 is an elevational View illustrating the manner in which .a helical gear is associated in the machine with the grinding wheel;

Fig. 7 is a view similar to Fig 64 but showing the relationship between the grinding wheel and a spur gear;

Fig. 8 is a fragmentary, transverse sectional View `talten on .the line 88 of Fig. 7;

Fig. 9`is an enlarged, vertical sectional View taken on the line 9`9 of Fig. 1;

Fig. 10 is an enlarged, transverse sectional view taken `on the line ylll-.lll of 3; and

Fig. 1'1 is yan .enlarged View oi the portion `oi Fig, 5 enclosed in the circle H.

Considered in certain of its broader aspects, the machine embodying the present invention comprises `a base 20 ywhich preferably is in the form of yan elongated, hollow casting. Mounted on the base .MJE adjacent one end thereof is an upright work head .column 22 which pivotally supports a swivel 124 for movement about .a horizontal axis. The latter, in turn, 4carries a. vertically slidable work spindle head '26 which has provision for holding and rotatably supporting a suitable workplece such as the spur lgear 28. Mounted on the base 20 "laterally .of work spindle head 2li is a slide base 3.0 which'supports a pairof superposed, independently movable slides 32 and Sli. Slide 32 carries :a grinding wheel 36 inoperative association with 'the workpiece 28, and slide 34 carries a crush roller dwwhlichiis .positioned in operative association with the grinding wheel (Figs. 2 and 4) With reference .to thewoperation of grinding the workpiece 28, it will be .observed that grinding whee'13l6 is formed with .a helical, peripheral cuttingthread which matches :thehteeth of the workpiece .'(Figs. 2 and `8),'and provision is made for advancing. :and retracting .slide 32 to bring the wheel and workpiece into voperative relationship. Suitable dri-ve means .is `provided for rotating grinding wheel ,.36 .at a relatively high speed suitable tor grinding. In this connection, speeds in the order of :5100 R. P. M. are satisfactory. This drive Amecl'ranisnfi also is operative to rotate work piece 28- in timed relation with grinding wheel 30 and simultaneously to slidablyactuate the work. spindle head .26 so'thatthe workpiece moves from the dotted-.line position to the full-line position in Fig. 4. Workp'iece 2-8 preferably rotates at a speed which ycauses it to advance or index one tooth fior every revolution .of vthe grinding wheel. For example, 4if lthe .grinding-Wheel at rotates approximately 15100 R. P. M., `a lgear having 48 teeth would be rotated approximately R. P. M. Manifestly, however, ythis ratiowill vary, dependlngfon. 'the Ynumber :of teeth :in lthe 'workpiece As:

best shown in Fig. 4, as the workpiece travels from the fullto the dotted-line position, its periphery moves across the cutting surface of grinding wheel 36, and, during such movement, its teeth mesh with the external thread of the wheel. In the case of the gear hereinabove referred to, the vertical travel should require approximately one and one-half minutes. During this travel, workpiece 28 rotates approximately 158 times, and, as it moves across the grinding wheel 36, its teeth are moved progressively and repeatedly against the grinding wheel. By reason of the iact that the gear teeth and the cutting thread complement each other (Fig. 8), stock is removed progressively from each tooth as it moves past the wheel, and both sides of the tooth are ground simultaneously. Thus no single surface of the grinding wheel does all the cutting as in conventional grinding machines; instead, the removal of stock is divided among a plurality of cutting surfaces and wear on the wheel is correspondingly distributed.

The above mode of operation produces generated ground teeth in a fraction of the time required by present-day apparatus. The grinding operation on each workpiece is continuous, and there are no idle periods taken up by the return stroke or by gear indexing as in conventional reciprocating-type grinders. Also, the speed of the traversing motion between wheel and work can be relatively great, since this motion is rotary and is not limited by unbalanced dynamic forces which place a denite limit on the operating speed of reciprocating types of gear-grinding machines.

With reference to the operation of dressing grinding wheel 36, the crush roller 40 is of substantially the same diameter as the grinding wheel and is formed with a peripheral surface which complements the cutting thread on the wheel. In the form of the invention here shown, where the cutting surface of the grinding wheel is a thread Aor helix, the thread on the grinding wheel has a left-hand pitch and the thread on the crush roller has a right-hand pitch. Provision is made for actuating slide 34 to bring crush roller 40 against the grinding wheel 36 with the threads of the two elements in accurately matched relationship. It will be obvious to those skilled in the art that the crush roller is of hardened steel or other suitable material capable of forming the grinding wheel. Also, a slow speed drive is provided for synchronously rotating the grinding wheel 36 and crush roller 28 in opposite directions so that the wheel is dressed as the roller is pressed thereagainst and for simultaneously rotating the work support in timed relation to the grinding wheel so that the relative rotary positions of the latter elements are not disturbed during vthe dressing operation. Any speed suitable for crush dressing can be employed, and this speed may vary somewhat, depending on the particular circumstances. In general, however, the surface speed of grinding wheel 36 and crush roller 46 should be about Z50-300 feet per minute.

For a m'ore detailed description of the invention, attention is rst directed to Figs. 3 and 4. Work-head column 22, swivel 24, and Work spindle head 26 are generally in the form of hollow castings and collectively contain and support certain of the actuating and driving mechanisms. It will be observed that swivel 24 is mounted on and rotatably supported by a xed bearing 42 which projects horizontally from the innerv ver'- tical wall of work-head column 22. Since the work-supporting head 26 is carried by swivel 24, rotative adjustment of the latter Varies the relative angular position of the workpiece 28 and grinding wheel 36. Such adjustment is necessary to match the teeth of the workpiece with the cutting thread of the grinding wheel. When grinding spur gears or the like, the swivel 24 is positioned so that the plane of the gear is disposed substantially parallel with the axis of the grinding wheel (Fig. 7) however, when grinding helical gears or the like, the swivel 24 is rotatably adjusted to position the gear at an angle to the axis of grinding wheel 36. A graduated scale 44 on the periphery of swivel 24 co-operates with a stationary reference mark 46 on workhead column 22 to indicate the rotative adjusted position of the swivel and workpiece. Radial flanges 48 at opposite sides of the work-head column 22 carry forwardly projecting studs 50 which extend through elongate-d slots in confronting radial flanges 62 on the swivel 24. Nuts 54 on the projecting ends of studs 60 are loosened to permit adjustment of the swivel and tightened to hold the same solidly in the selected adjusted position.

As shown in Fig. 2, the work spindle head 26 is formed with a vertical guideway 65 which receives and is slidable on a vertical guide or track 58 provided on the swivel 24. Manifestly, the vertical travel of head 26 is small, since its only purpose is to move the workpiece 26 across the cutting race of grinding wheel 36. A typical example of this movement is shown in Fig. 4 wherein the workpiece 28 is moved from the dotted-line position to the full-line position, and the distance between these two positions constitutes the vertical travel of the work spindle head 26.

When grinding a plurality of identical gears it is desirable that the work spindle head 26 occupy the same starting position for successive operation. This is particularly important in the case of helical gears. According to the present invention, the operator is able to reset head 26 quickly and accurately after each grinding operation by reason of a suitable gage which is mounted on the front of the machine. This gage indicates visibly when head 26 reaches the initial or starting position and comprises a depending lever 6!) which is mounted for rocking movement about a horizontal pivot 62 on the head. Also mounted on head 26 is a dial indicator 64 which engages the lever 60 to hold it normally against a stop 66. When the lever 66 is against stop 66, dial 64 registers a zero or neutral position, and, when the lever swings to the right the extent of such movement is registered on the dial. At the lower end of lever 60 is a lateral V-shaped extension 6B, and this extension is positioned to engage the V-shaped end 16 of a dog 12, the latter mounted on the swivel 24 and vertically adjustable in a key slot 14. Thus, when work spindle head 26 is lowered on the swivel 24, the extension 68 engages the end 10 and, by reason of the incline-d interface therebetween, rocks lever 60 to the right. As suggested, this movement is registered on dial 64, and the mechanism for lowering head 26 is stopped when the dial registers the starting position. As a precautionary m'easure to prevent jamming oi the indicator dial 64 in case the work spindle head 26 is lowered inadvertently beyond the desired starting position, the extension 68 is of such llength that it can ride safely past the dog 12.

It is contemplated that head 26 be raised at actu-ated rnec'lians' I ally for resetting. T after described in detail'. v

As shown in Fig. 1, the weekly-spinne head 2s is formed at-itslowerend with 'lateiaily extending portion 16 which Carries meeha sin for rotatably supporting" and '-detachabl-S'f' stamping' a workpiece-28. Thism'eelia is'infisshownI- in- Fig'. 4 and compri-'se a v ily dispesed, tubulairv work spindle 'I`8`- its end-s by bearings 8'@ 'and 82?. upper endof spindle 18 ext" aboveI the portion T6 and supportsVv a W'oik talled'w eh bolted orotherwise fastened thereto.v Su ount'ing" "ther` work tatie 84 and fast' nedftnerete by bolts' at is a werk-holding nir-ture 8'8. 'The latter is formed with a depending puetoo'w norma-uy nts-,in a pilot hole g2 'pro ideti'l ra y in tliet'able M. Workpiec'e 28 there' sh by' way' of example as a spur ge'ari" restsionth trop; surface of nature es and is eentere'd'tvtn its' `tere a 'pilot 92 whichI is' integraliwithlfand pr'jeet's'- upwardly from the'iixtura In Order to -holcll the' "workpiece 28 solidly 0n iixture 881 during the grinding operation and 'to' render it easily and removable at the end of such operation, adraw' ro'dltli's`l mounted for verticalV sliding' -rnove'xhent -the tubular spindle T8- andfin aligning boresyprovided Ycentrally in the table andi 'fiitfire 'Draw rod 94' extends upwardly through ene phot 9*2, and the projecting portion thereof carries-nuts' '9G which conne a clamping 'plate 'I-he latter 'rests on workpiece Zegna-preferably 's'in'vv the form f a; G-'Washe sth'ateit be easily and quickly removed from or appliedtofridy 94 without re'- moval of nuts -St- The-lower fendj of draw rod et extends from spindle 18', and the projection port-'ionl thereof "carries a fixed? radially extending follower ltiif'tvhichco-operates with the adjacentendof the spindle'toc""'inel an annular sei-ies of compression springs-W21. 'These springs m25 Costantlyuige draw Arbd Q'owriwardly and with-suflcient lforce sothatjnut's 'Maud-clamping plate 98gh0ld workpiece '248i Vsolidly against the xtur'e 'during the en efcycle" oi"- operation.

Manifestly, it is" re essai-y t'o-forc'erdraw vrod 94 upwardly agaih'stthuton df's'pings |02 in order to release wor "ece 28"'. According to the present invention this'fisaccoinplished YAby a cam not which is fixed on a 're-ek shaft `'Interni Aseats the lower end of the draw rod (Fig. 5). Shaft i106 is' supported by spaced llearings US in a Supporting lor-'aok't H0. Ait its forward end the' rock shaft carries faiinamiallyoperable lever H2, The peripheral?surface`of'-carh NT4 is arranged` eccentricallly toi 'the axis ofrock shaft tot sol that vmovement' or "handle 'l la in one' directionz forcesv thedrawfrodl SBHpwa'rdly' torelease workpiece 28=andffoyemeift thereof inl the opposite direction permitsfs'prng's m2" to lower thev draw rodan'dL-clanip 'th'eworlipiece' solidly on fixture 83. "Lever |"l22i'normally-i's positioned and its movement restri di by' a 'Il' which' is embedded in the`"loraeket IvIF-ad-Lprojects' forwardly thioigli'arieloigeitd "otlat Slot' HTG in the leve-r; Y,

From' the foregihfg't-Wilill be readily apparent that the WerkSlllrldlg'lieatl 26 I'f lprb'c'ates or tralisl'ates workpiece 28 ailve's 'ta'c-s the cutting face'of grindingwhielGiandltlitspntdle 78' rotates vthe "workpiece dui'l'g Vertical movement. The rate and extent of translatory @redirigerti-ifrne'cha is' herein'- (it)y 6 of the' workpiece; however, as suggested., the workpiece must be rotated intinledrelation' with the grinding wheel, and the mechanism for accomplishing this end is hereinlaft'er described in detail'.

During the grinding operation'` coolant'is circulated by a pump E20 from a suitable reservoir through an eduction tubing 22 which discharges above the work as shown' in Fig. l. The system for circulating the coolant is 'conventional and need not be described in detail'. In the apparatus here shown by way of illustration, the hollow base casting 29' serves as a reservoir for the coolant, and the pump l2?! is mounted directly thereon, as shown in- Fig. e. A suitable guard L23 in front ofy grinding wheel te andV crushroller it prevents the operator from being splashed by coolant and also prevents him from physical-ly contacting the wheel and roller.

In order to control the relative rotary positionof workpiece 2t and the fixture te and to insure identical positioning of similar workpieces, an arm l 24 is supported for pivotal movement about a vertical axis and in horizontalalignment with the Work by a suitable bracket E26 on the work spindle head '261 A locator |218 carried by and longitudinally adjustable along the anm IM is shaped toy engage vbetween adjacent teeth of workpiece 28' when the arm is'positioned as shown in Fig. 2. However, a torsion springr ite (Fig. 3) normally actslx on the arm lift to swing it outwardly away from the workpiece so that it is unobstructi-vely positioned during the grinding and setting up operations.

lIn practice, the rst of a series of identical gear forms is mounted on vvthe fixture 88 yandma'tched with the proiile of grinding' wheel 36 before it is clamped. After the relative positions of the workpiece and grinding 'wheel have been established in this manner, the workpiece is clamped on the xture, the grinding operation is performed, and the grinding Wheel is stopped in a predetermined initial position vby means hereinafter described in detail. Arrn mi is then swung toward the workpiece, and locator l28 is mounted on a horizontal spindle E32 which in turn is journaled for rotation in a tubular housing |34. The latter is formed integrally 'with or mounted on the slide 32 and is located so as to position the axis of the grinding Wheel substantially midway between the extreme upper and lower positions of the workpiece (Fig. 4). Spindle 32 extends through housing |34 for driven engagement with driving mechanism hereinafter described in detail.

In order to enable the operator to bring grinding wheel .it to the'pr'e'dete'rrn'ined initial position, a disk i355 is x'ed on the projecting rearward'portion of spindle i321. This disk projects above' housing l'fi, and vthe projecting marginal portion thereof is provided with a suitable reference rnark (not shown) which registers with a stationary reference `mark l38on housing i3d when grinding wheel 36 is in the selected position.

=In` order to adjust grinding-wheel to the proper depth for eut, mechanism islprovideu f for moving slide 32 longitudinally on slide base 30, and this mechanism comprises a feed screw |40 which is supported by stationary spaced bearings |42 (Fig. 4). At its inner end the feed screw i43 threadably engages a depending lug |44 on slide 32. At its outer end feed screw |49 carries a manually operable hand wheel |46. Thus, slide 32 is advanced or retracted by manually rotating hand wheel |46, and the periphery of the wheel is lprovided with a graduated scale |48 (Fig. 2) which co-operates with a stationary reference mark |56 on bracket |52 to indicate the adjusted position of the slide.

Feed screw |49 has a relatively fine thread to secure accurate adjustment or slide 32. Consequently the rate of travel of the slide is slow when actuated by hand wheel |45. In order to back grinding Wheel 39 rapidly away from workpiece 28 after the latter reaches the upper limit of its travel, bearings |42 are mounted in an externally threaded sleeve |54, which sleeve operates in an internally threaded supporting bracket |56 mounted on the slide base 36. Sleeve |54 is r0- tated by a, manually operable lever |59. The external thread |69 of sleeve |54 has a Very long lead so that the sleeve is moved rapidly in an axial direction when rotated. At its outer end sleeve |54 is formed with an enlarged head |62 which seats against bracket |56 to limit forward movement of the sleeve and to assure identical positioning of slide 32 when the sleeve is fully advanced.

Thus hand wheel |46 can be used to obtain a fine adjustment of grinding wheel 36 relative to workpiece 28, and handle |59 can be operated to retract the grinding wheel and slide assembly rapidly after each grinding operation. In addition, after each new workpiece 2S is clamped on the xture 88, handle |58 can be actuated for rapid traverse of the grinding wheel assembly toward the work, and the arrangement is such that the grinding wheel is returned to precisely the same position after each operation.

Crush roller 46, which is of substantially the same diameter as the grinding wheel 36 and is made of hardened steel or other suitable hard material, is mounted on spindle |64 which in turn is journaled for rotation in a horizontal tubular housing |66 fastened to or formed integrally on the upper slide 34. As shown in Fig. 4, the slide supports the roller in horizontal alignment with grinding wheel 36. Thus the arrangement is such that slide 34 can be advanced to bring the crush roller 49 into peripheral engagement with grinding wheel 36 for dressing the latter.

Provision is made for assuring proper matching or engagement of the threaded peripheral surfaces of the grinding wheel 36 and crush roller 49 and for rotating the wheel and roller synchronously in opposite directions at a suitable rate of speed.

Provision also is made for feeding the crush roller 4|) under power against the grinding wheel 36 and for manually advancing and retracting slide 34 to engage or disengage the power drive. This mechanism is shown in Fig. 4 and comprises a feed screw 63 which is journaled for rotation in a suitable bracket |19 bolted or otherwise fastened at the outer end of slide 34. The threaded inner end of screw |68 operates in an internally screw-threaded lug |12 mounted on and xed to the subjacent slide 32, and the outer end thereof carries a hand wheel |14. Thus, slide 34 is advanced or retracted, depending upon which direction hand wheel |14 is rotated. The adjusted position of slide 34 onslide 32 is indicated by a stationary reference mark |18 (Fig. 2) which cooperates with a graduated scale |16 on the periphery of hand wheel |14.

The high speed rotary drive mechanism for operating workpiece 28 and grinding wheel 36 in timed relation with each other and for simultaneously raising the work spindle head 26 at a predetermined constant speed is now described in detail. The driving power for this mechanism is supplied by a motor on the stationary work head column 22. The drive shaft |82 of the motor is connected to a sleeve |84 by pulleys |86 and |88 and an endless belt |90. Sleeve |84 is journaled for rotation in a horizontal housing |92 and is connected by a conventional multiple disk clutch |94 to a countershaft |96 which is journaled in and extends between a gear housing I 98 on the work-head column 22 and a gear housing 239 on the grinding wheel housing |34.

The right-hand or inner end of countershaft |96 rotatably drives the grinding wheel 36. As shown in the drawing, shaft |96 carries a sleeve 262, and a splined connection is provided between the shaft and sleeve to accommodate movement of the slide 32. Sleeve 202 in turn carries a bevel gear 264, and this gear meshes with a bevel gear 296 on the grinding Wheel spindle |32. Gears 264 and 266 may be in any desired ratio, but in any event the ratio should be such that grinding wheel 36 is driven at a suitable grinding speed in the order of 5100 R. P. M.

The left-hand or outer end of countershaft |96 rotatably drives the work spindle 18 and also drives mechanism for raising the work spindle head 26. As shown in the drawing, shaft |96 carries a pinion 268 which drives reduction gears 2li), 2|2, and 2|4 in the gear housing |98. The reduction gearing, in turn, transmits motion to a driven shaft 2|6 through change gears 2|8, 220, 222, and 224. Access is had to the change gears through an opening 226 in housing |93, which opening is normally closed by a removable cover 226. As best shown in Fig. 3, shaft 2|6 is journaled adjacent its ends in bearings 42 and 230, and its inner end drives a vertical shaft 232 through bevel gears 234 and 236. Shaft 232 is j ournaled in and held stationary by spaced bearings 238 and 24|). Its upper end drives the mechanisni for raising the work spindle head 26, and its lower end drives the mechanism for rotating the work spindle 18.

The latter mechanism is rst described, and it will be observed that the splined lower portion of shaft 232 drives a vertically slidable sleeve 242 which carries a spur gear 244. Sleeve 242 is journaled in a supporting housing 246 and the latter is fastened to the work spindle head 26 by bolts 243 so that it and the elements carried thereby move vertically with the head. Housing 246 also rotatably supports an idler gear 256 which meshes with gear 244 and drives a spur gear 258 (Fig. 4). The latter gear is keyed or otherwise fixed on the work spindle 16 and is held solidly against a radial shoulder 260 by a retainer ring 262 so that it also moves vertically with the head 26 and spindle. Thus, workpiece 29 and grinding wheel 36 are rotated simultaneously from opposite ends of countershaft |96 but the workpiece is rotated at a much slower rate of speed than the grinding wheel by reason of reduction gears 2|!l-2I4 and change gears 2|6 224.

As suggested, the speed at which the workpiece .2,58 rotates varies :according to :its size .and usually is determined .asa :function of the number of teeth in 'its periphery. This .sneed ,can be acllusted aecerdiine .f5.0 the @Xighoies of 4the Aparticular .situation by #Varying the ratios of change gea-rs Zita-224. Although lthe xdevice vwill operate .satisfactorily over a range of ratios between 4the workpiece 28 and grinding wheel .35, it is pre- @erred that the ratie'be such that the :workpiece advance `one tooth for each revolution .of the grinding wheel.

*During operation of the machine a :dra-g is .produced .on the spindle 1t8 to prevent reversal of back lash yin lthe driving gears when the spindle is stopped, hy 'means -of 'a brake shoe 264. As shown in Fig. 4, brake shoe 265 is urged against 'spindle 18 by Aspring 266, and the ypressure exerted by the spring is Aregulated by an adjustable thumb screw 268.

The mechanism :fer :raising work vspindle head now .described :comprises -a vertical feed screw ,21E whichis -driyen romshafi-t 232 through reduction gears 212 and 214 and change gears 216, 218, 28u, and 282. The reduction .sears i212 .and `214 are disposed :in the 4swivel '24 and the change gears 21:6--2182 .are :suitably `journaled and supported in a` housing .28.4 on the swivel. Access is to the change gears rior varying the speed at which fthe work spindle head :26 travels to trans.- late the work 28 by ,means of .a Aremovable vcover 2.86. When ,grinding helical sears, :the `head 35 must be .actuated to more the `work axially in timed relation fto the rotative sneed of the wheel and work inlordertooompensate .the lateral component of movement -o-f the work as it traverses the. grinding wheel and to maintain proper :rneshed engagement .between the near -teeth yand the 4cutting thread .of the Wheel. Accord-ing to the present invention, .the -W-or-k is moved positively in an axial direction by the gear tra-in .hereinabove referred to, and the sneed 'at which it travels yhan be varied by changing the gea-r ratios between change gears 21B-28.2. .As best "sho-wn in 5, .feed screw 21D extends into the head 26 `and* a `portion thereof with-in .the head is externally threaded .as at `238. Mounted .on portion 288 :is aninternal-ly threaded nut 29B which .Supported in a `,tubular housing 292 by fs-paced bearings .294. The housing is bolted or otherwise fastened to work yspindle head 2B so `that `the latter is :slid-ably -actuatedeitherwhen :the feed screw 2101s lrota-ted- .and 'nut 2.90 is held against rotation or when the feed screw is held .stationary and :the nut is rotated.

.For power actuation (of head 256, the nut '290 is held stationary and -feed screw 21.0 is rotatably .driven in the manner hereinabove described. In this connection a suitable ,clamping mechanism is provided for 'the nut, which mechanism conveniently may be of the 'type shown in Fig. 1 0. The clamping mechanism here shown comprises a horizontal-shattZS- Whehextendsinto head .laterally of :mit .29d-and is. iournaled for rotation on suitable sunpontng hearings ,2.9.8. Fixed on the sha-ft: ,29.6 .at opposite sides of the .29.0 `.fa-re identical eccentric .earns 3.100 which carry collars .a02 having shanknortions ,3204 .slidably journaled in hearings 3.85 andioinedbv n o.let-mening bar -30-6. .It will be 1obsewed .shait .296. Land clamping .3.0.5 yare :arranged at oppositefsides of rnut .290, and fit :will be readilyapparent that the clamping har can be tightened against. orreleased :from ,the A:out by rotating shaft 2.9.6.. .This latter operation `is. .accomplished ,byl means of. .a ttmanually .operable handle '30.8 von :the forward end Aoi' shaft ,29.6.

110 Thus, to raise head 26.. thenower drive :is operated. :to rotate feed screw ,210, and handle 3de is actuated to clamp hut 29.0.. A-s a result, the nut moves 4 upwardly on :feed screw 21B and carries 5 ythe head 2:.6 alone with it. When :head 26 moves upwardly, workniecez is moved .across the cutting race ,of erndirigwheel 316.

After each .grinding .operation is completed. the work spindle rhead .26. is lowered manually by a hand `wheel .B110 which `is mounted on a .shaft SI2 and operates bevel shearsy 3M .and :316. As shown Fg- 5, S31-raft '312 is johrnaied for rotation in .head :2.6, gear A3.115 .fast `en the inner end of the shaft, andgear .SI5 fis fixed fon the upper end of nut.29,0. Manual retumof the-Workspzndle .head 2.6 is necessary., since the power drive mechanism, hiel-udine yfeed screw 210. is stopped after the grinding opera-tion and it is necessary to .lower the head before the 1`next grind-ing operation is fbgun.

Lowering the Work head 26 ir-1 the above manner tends to reverse :the back lash in all of the ,sears which .drive feed screw 210.; and, to prevent lthis action, a free wheeling clutch 3 I8 of known construction is mounted between the feed screw and the driving .spindle or shaft 319 .of gear 28.2 (Fig. 3). clutch .allows feed screw 210 to turn freely inzone direction -for Vfeeding the work spindle head 2;5 upwardly but prevents the same from rotating in the opposite direction. After work :spindle head .26 has been lowered to the initial or starting position as indioatedfon .difal 65, handle 5308 isoperated to :clamp nut 2&0 and the mecha- -is again `set for power operation.

The slow-speed drive mechanism ffor synchronously rot-ating grinding wheel 36 and crus-h rol-1er .et and for siinuitanecusly pressing the latter again-st the grinding wheel is described. As leest shown in Fig.. 2, the motor t8!) is provided with van integral ,gear head 5.3.20 having a slow- '.Speed -dnive shaft 32.2 which drives a sleeve 32u through pulleys .326. and 3.28 .and an endless belt 5.3.3.0.. Sleeve `-3:24 is associated Muth the Ymultiple disklntoh i911 in .the same manner as sleeve las. is Thus, the arrangement :is 4such that clutch I9@ can be .oneraztedito disconnect hoth .sleeve 1:84 and sleeve v.e215 .simultaneously Afrom .shaft :las lor to selectively connect either of these sleeves to :the shaft.

As shown in lig, 19, .clutch .16914- is. operated by .aies/1er 332 wlzrlichA is .carried by a rock shaft 33st. The .latter is rotatably supported .by work-head column .20 .and is arranged horizontally under the clutch. At. the inner .en-d :of rockshait 334 isy an .upstanding dog 3,35 which engages the clutch shiter '33.8. When handle 13352 is positioned upright asshown .in .fthe'drawing, clutch 194i is in neutral Iposition .and fceuntershaft 'las is stationary; when the handle is movedtothe left, sleeve. ladisnoupled to the countershaft for high- .speed operatien;v and.. when Athe `lever is moved to fthe: right., sleeve 3256 iswcoupled tothe countershaft for slow-speed operation.

Thus, in the latter .position of handle 33 2*, grind- 85 ing vWheel 3 6 'is rotatabiyxdriven relatively .slowly atiaspeed suitable 'torzcrush dressing. yThis speed may vary, .depending .on :the circumstances, but speeds: in .the onder of 16u-19.0 R. P. M. have been ioundfto vhe mostasaztisiaetory for grinding Wheels of. `the size andztype here shown. f

Assuggested. ithe :crush .roller 4D is not actuated whenslide 34 :is retracted. In order :to dress Vthe :grinding wheel 3.5, tit :is vnecessary initially to advance slide .34' :by A.manually .actuating hand wheel lill-in the .mannerdesoribed As .shown in 1'1 Fig. 2, slide 34 is equipped with a drive shaft 340 which is disposed in alignment with countershaft 96 and is supported adjacent its ends by bearings 342 and 344. Shaft 34D projects into a gear housing 346 on housing |66 and carries a bevel gear 348 which meshes with a bevel gear 350 on the rearward end of the crush roller spindle |64. Mounted on drive shaft 340 ahead of gear 348 is a clutch element 352 which is positioned to engage a second clutch element 354 on countershaft |96. The latter clutch element is slidably and rotatably xed on countershaft |96, and, although clutch element 352 is rotatably fixed on drive shaft 34D, it is adapted for limited sliding movement and is preloaded by a suitable compression spring 356. The two clutch elements 352 and 354 engage just before the crush roller 46 contacts grinding wheel 36, and the dogs which lock them together are unevenly spaced so that they can interengage in only one relative rotative position, viZ., when crush roller 46 and grinding wheel 36 are positioned to engage properly with each other. Manifestly, if clutch 352 engages clutch 354 when the dogs are out of register with each other, the former slides on drive shaft 346 against the action of spring 356 until the latter clutch element rotates suciently to effect proper engagement. When clutch elements 352 and 354 are engaged, crush roller 40 is driven synchronously and in the opposite direction to grinding wheel 36, and drive shaft 346 is rotated directly with countershaft |36.

Once clutch elements 352 and 354 are engaged, it no longer is necessary to actuate slide 34 manually, since shaft 340 also drives mechanism for automatically slowly advancing the slide (Fig. 5). The automatic mechanism comprises an eccentric 358 which rotates with shaft 340 and actuates a pivoted pawl lever 360 through a connecting link 362. A pawl 364 pivoted on lever 360 operates a ratchet wheel 366 which is keyed or otherwise rotatably fixed on feed screw |68.

In operation, the eccentric 358 acts through link 362 to oscillate the pawl lever 360. The latter, in turn, actuates pawl 364 to rindex the ratchet wheel 356 and produce a slow feed motion of slide 34. A stop pawl 368 keeps ratchet wheel 366 from reversing when pawl 364 moves back over the ratchet teeth after each advance.

In order to release the ratchet wheel 366 for manual return of the slide 34 by hand wheel |14 after the dressing operation, a freely rotatable pawl lifter is mounted behind the ratchet wheel for simultaneously disengaging pawl 364 and stop pawl 368 from the wheel. Pawl lifter 310 is actuated manually by a handle 312 which normally is held against a stop 314 by a spring 316 to hold the pawl lifter disengaged from the pawl and stop pawl members.

In operation, handle 312 is depressed to disengage pawl 364 from ratchet wheel 366, and this action stops the automatic power operation of slide 34. The latter can then be retracted manually by hand wheel |14. As soon as slide 34 is retracted sufficiently so that clutch elements 352 and 354 disengage, handle 312 can be released. Spring 316 then raises the handle automatically and releases pawl 364 and stop pawl 368 so that they again engage ratchet wheel 366. Thus when handle 312 is released, the parts are positioned automatically for power operation of slide 34 when it is again advanced to engage clutch elements 352 and 354. Manifestly, the crush roller 46 ceases to rotate when clutch element 352 disengages clutch element 354, and, since clutch disengagement also renders inoperative the automatic power-drive mechanism for slide 38, the crush roller is not fed toward the grinding wheel 33 when grinding operations are resumed.

During the crushing operation, countershaft is still connected to the work spindle head feed screw 210 so that the work spindle head 26 moves upwardly. However, by reason of the reduced speed at which countershaft |96 is operated and the reduction gearing intermediate the countershaft and feed screw 216, the upward movement of head 26 is very slow. Ample time is thus provided to complete the dressing operation before head 26 reaches the upward limit of its travel. In any event, head 26 is lowered manually by hand wheel 3|0 to the initial position after the dressing operation. It is desirable that the feed screw 21|) be operated continuously during the dressing operation in order that the relative rotary position of the grinding wheel 36 and the work spindle 18 be not disturbed as would be the case if the work spindle were disconnected from the drive at this time.

It is to be understood that the form of the invention herewith shown and described is to be taken as the preferred example of the same and that various changes in the size, shape, and arrangement of parts may be resorted to without departing from the spirit of the invention or the scope of the appended claims.

Having thus described the invention, I claim:

1. In a continuous gear-grinding machine, the combination of work-supporting means including mechanism for simultaneously rotating and translating the work; a grinding wheel having a peripheral cutting surface shaped to complement the surface of the work to be ground, and adjustable so that said cutting surface moves across the work during translatory movement of the latter; a crush roller mounted in proximity to said grinding wheel having a dressing surface which complements the cutting surface of said grinding wheel; means for adjusting the grinding wheel and work into operative relation with each other; means for moving the grinding wheel and crush roller into operative relation with each other; drive means for rotatably driving the grinding wheel and work-supporting mechanism in timed relation and for simultaneously translating the work-supporting mechanism in one direction to move the work across the cutting face of the grinding wheel; and drive means for simultaneously rotatably driving the grinding wheel, crush roller and work-supporting mechanism in timed relation, said drive means constructed and arranged to rotate the grinding wheel and crush roller in opposite directions and at the same peripheral speed, and said work-supporting mechanism being rotated in timed relation to but slower than the grinding wheel and the crush roller.

2. In a continuous gear-grinding machine, the combination of work-supporting means including mechanism for simultaneously rotating and translating the work; a grinding wheel having a cutting surface and arranged so that said cutting surface engages and traverses the work during translatory movement of the latter; a crush roller normally disengaged from the grinding wheel but movable against said cutting surface to dress the same; means for rotatably driving the grinding wheel at a predetermined grinding speed and in a predetermined ratio to the rotative speed of the work; and means for rotatably driving the crush roller and grinding wheel in synchronism slide is advanced by said manual actuator means and to disconnect the same when the slide is retracted by said manual actuator means; means for transmitting motion from said one drive shaft to the crush roller, and means for transmitting motion from said one drive shaft to the feed screw, whereby said slide is manually actuated to engageor disengage the clutch elements and whereby said crush roller and said slide are power-actuated when said clutch elements are engaged.

1l. In a continuous gear-grinding machine, the combination of a rotatable grinding wheel having a helical peripheral cutting thread; means ior rotatably driving the grinding wheel at a predetermined grinding speed; work-supporting means for rotating work to be ground; means for rotatably driving said work-supporting means vin timed relation to the grinding wheel; a crush roller having a peripheral thread shaped to mate with and opposite hand to the cutting thread on said grinding wheel; means for moving said grinding wheel and said crush roller into operative relation; and means operable independently of said first drive means for simultaneously rotating the grinding wheel. crush roller and worksupporting mechanism at a predetermined speed slower than said grinding speed and suitable for crush dressing said wheel, said .last means operable to rotate the wheel and roller in synchronisin and in opposite directions and to rotate said work-supporting means in timed relation to but slower than the wheel and roller.

12. In a continuous gear-grinding machine, a grinding wheel; a crush roller; means for moving said grinding wheel and said crush roller translatively into and out of peripheral engagement; mechanism for rotatably driving said grinding wheel; mechanism for rotatably driving said crush roller; and clutch means for connecting said drive mechanisms; said clutch means constructed and arranged to disengage said drive mechanisms when the grinding wheel and crush roller are a maximum distance apart and to engage said drive mechanisms when the grinding wheel and crush roller are moved toward each other prior to actual contact between the wheel and roller.

13. The combination as set forth in claim 12 wherein said translating means is correlated with said clutch means and said rotary drive mechanisms so as to be manually operable when said clutch means is positioned to disengage said rotary drive mechanisms and to be mechanically operable when said clutch means is positioned to engage said rotary drive mechanisms.

14. The combination as set forth in claim 12 wherein said clutch means is engageable only when said grinding wheel and said crush roller are in predetermined rotative positions with respect to each other.

15. In a continuous gear-grinding machine, a grinding wheel; a crush roller; a slide carrying said crush roller and operative to move the same relative to said grinding wheel; a first mechanism for rotatably driving said grinding wheel; second mechanism for rotatably driving said crush roller; clutch means for connecting said rst and second drive mechanisms for mutual operation when the slide is actuated to move said crush roller into operative relation with the grinding wheel; and means actuated by said first drive mechanism for moving said slide in a direction to advance said crush roller toward said grind-- ing wheel.

16. In a continuous gear-grinding machine, a grinding wheel; a crush roller; a slide carrying: said crush roller and operative to move the sanzc relative to the grinding wheel; a first mechanism for rotatably driving said grinding wheel; a second mechanism for rotatably driving said crush roller; clutch means for connectingl said first and second mechanisms for mutual operation when the slide is actuated to move said crush roller into crushing relation with said grinding wheel; rapid traverse means for actuating said slide; and automatic means driven by said second rotary drive mechanism for actuating said slide to feed the crush roller relatively slowly against said grinding Wheel.

17. The combination as set forth in claim 132 wherein said rapid traverse means is manually operable and constructed and arranged both tc advance and to retract said slide whereby to engage or disengage said clutch means; and wherein said automatic feed mechanism is operable only to advance said slide and only when said clutch means is engaged.

18. In a continuous gear grinding machine, a work; supporting means; a grinding wheel for mutual peripheral engagement with work on said supporting means; a slide carrying said grinding wheel operable to move the same relative to said work supporting means; and two-part means for actuating said slide comprising a manually operable screw threadedly engaged with said slide, a stationary member and a manually operable screw threaded on said first screw and threaded into said stationary member; said rst screw being constructed and arranged to move the slide relatively slowly and' to selectively position the same a predetermined distance from said work supporting means, said second screw being constructed and arranged to retract said slide relatively rapidly from said selected position and to advance the same relatively rapidly from a retracted position to said selected position.

19. The combination as set forth in claim 18 wherein said first-mentioned screw has a relatively short lead, and wherein said second-mentioned screw has a relatively long lead.

PAUL KLAMP.

REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 1,008,838 Lundgren Nov. 14, 1911 1,640,993 Hanson Aug. 30, 1927 1,642,554 Olson Sept. 13, 1927 1,693,781 Hanson Dec. 4, 1928 1,720,620 Bayton July 9, 1929 1,753,448 Smith Apr. 8, 1930 1,823,734 Garrison Sept. 15, 1931 1,985,213 Page Dec. 18, 1934 2,178,022 Orcutt Oct. 31, 1930 2,307,238 Ross Jan. 5, 1943 2,385,650 Rickenmann Sept. 25, 1945 2,424,191 Rickenmann July 15, 1947 FOREIGN PATENTS Number Country Date 520,557 Great Britain Apr. 26, 1940 

